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US3045447A - Rotary device, such as refrigerating machine or similar device - Google Patents

Rotary device, such as refrigerating machine or similar device Download PDF

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Publication number
US3045447A
US3045447A US795530A US79553059A US3045447A US 3045447 A US3045447 A US 3045447A US 795530 A US795530 A US 795530A US 79553059 A US79553059 A US 79553059A US 3045447 A US3045447 A US 3045447A
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United States
Prior art keywords
pressure
inlet
expansion
slide
rotors
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Expired - Lifetime
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US795530A
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English (en)
Inventor
Wagenius Hans Borje
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Svenska Rotor Maskiner AB
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Svenska Rotor Maskiner AB
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Publication date
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/16—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/10—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F01C20/12—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F01C21/186—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet for variable fluid distribution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/14—Power generation using energy from the expansion of the refrigerant
    • F25B2400/141—Power generation using energy from the expansion of the refrigerant the extracted power is not recycled back in the refrigerant circuit

Definitions

  • the present invention relates to a rotary device, such as a refrigerating machine or similar device; More particularly the present invention is concerned with a rotary device of the helical type provided with at least two cooperating male and female rotors having helical lands and grooves intermeshing with each other, and with a casing having intersecting bores for the rotors and end walls and inlet and outlet openings, in such a manner that the rotors upon their rotation together with the housing form closed expansion chambers, each comprising grooved portions in communication with each other of pairs of co-operating rotors and varying in volume as the rotors revolve.
  • An expander should be designed to be able to operate with high efiiciency at various pressure ratios between the admitted and discharged media.
  • the problem then arising in an expansion machine of the type referred to is due to the fact that the expansion occurs in a confined chamber shut off from the inlet as well as from the outlet so that the pressure ratio, i.e. the built-in pressure ratio of the device, obtained between the medium admitted into the expansion chamber and that discharged therefrom, is not dependent of the absolute pressure prevailing in the inlet and outlet sections of the device, respectively.
  • the expansion chamber is provided with a variable inlet opening which according to the invention an increased opening causes the covered axial length of the rotors to decrease and thus a decrease of the built-in pressure ratio and an increase of the volume flow, and a decreased opening causes the covered axial length to increase and thus an increase of the built-in pressure ratio and a decrease of the volume flow
  • a variable inlet opening consists in using an adjustable slide.
  • a suitable embodiment of such arrangement comprises an axially movable slide which when moved will expose a variable portion of the threads of the rotors.
  • this slide is provided with two envelope surfaces which closely contact the periphery of each rotor.
  • the end of the slide facing the inlet opening is further equipped with a recess which is provided with two edges one in each of the two envelope surfaces, said edges being parallel with the cams of the rotors and reciprocally displaced along the line of interamino Patented July 24, 19s2 section between the envelope surfaces a distance corresponding to the axial distance between two cams engaging each other of the male and female rotors, respectively.
  • a recess which is provided with two edges one in each of the two envelope surfaces, said edges being parallel with the cams of the rotors and reciprocally displaced along the line of interamino Patented July 24, 19s2 section between the envelope surfaces a distance corresponding to the axial distance between two cams engaging each other of the male and female rotors, respectively.
  • Control of the expansion device should preferably be automatic in relation to the pressure in the inlet, since the pressure in the outlet has to be maintained comparatively constant irrespective of the altitude. Therefore it is an advantage to arrange control means which are directly influenced by the pressure in the inlet of the expansion device.
  • a particularly suitable embodiment may be obtained by allowing the control means to operate in correspondence to the pressure difference between the pressure of the operating medium in the inlet and the pressure of a reference medium, which conveniently may consist of the outside air surrounding the aircraft.
  • the control device comprises preferably a balanced piston, on one side actuated by the operating medium in the inlet and on the other side by the reference medium, while the balancing of the piston is accomplished by means of one or more springs.
  • the piston may, if the control means are designed in a suitable manner be directly-connected with the slide, although a gear arrangement designed in one way or other may be required, particularly if the slide is not axially movable but instead thereof a slide arrangement of one or more angularly adjustable slides is substituted.
  • Another manner of controlling the dimension of the inlet opening is to use a slide adjustable by means of a speed regulating device driven by the expansion device.
  • the operating medium for the expansion device consists preferably of air supercharged in a compressor which forms an integral part of the aircraft power unit.
  • FIG. 1 shows a longitudinal section through one embodiment of the invention along the line 11 in FIG; 2.
  • FIG. 2 shows a cross-section through the same embodiment of the invention.
  • FIG. 3 is a diagram showing thelosses when the builtin pressure ratio does not correspond with the actual pressure ratio.
  • FIG. 4. is a diagram showing in what manner the slide is moved in relation to the pressure difference between the air in the inlet and the surrounding air.
  • FIG. 5 is a diagram showing in what manner the efiiciency will vary with the actual pressure ratio in expansion machines of two dilferently built-in pressure
  • the housing 10 of the expansion device is provided with an inlet port 12 and an outlet port 14.
  • the operating medium supplied to the inlet port consists suitably of air taken from the compressor of the aircraft power unit, said air prior to the inlet of the expansion machine being passed through a cooler.
  • the air additionally cooled by v it is supplied via an inlet opening 18 to the expansion chambers each comprising two grooves 20, 22 in one male rotor 24 and one female rotor 26, respectively.
  • the male rotor is equipped with four lands 28 located mainly outside the pitch circle of the rotor.
  • the female rotor is in addition equipped with six lands 30, mainly located inside the pitch of the rotor.
  • the lands 28, 30 extend helically along the rotor 24 and 26, respectively, and have rounded profiles which roll off against each other without reciprocal sliding.
  • each one of the rotors is provided with a synchronizing Wheel 32, which wheels engage each other and cause the rotors 24, 26 to revolve in relation to each other without direct reciprocal con-tact and resultant danger of seizing.
  • the male rotor 24 is provided with a shaft end 36 extending through the housing and on which a fan Wheel 38 is carried, said fan wheel being intended to brake or unload the power generated in the expansion device.
  • the size of the inlet opening 18 is adjusted by means of an axially movable slide 40 which is carried by means of ball bushings 42 on a pin 44 fixed to the housing.
  • a ball bushing consists of a sleeve with a number of closed ball races extending axially and filled with balls.
  • Each ball race consists of one operating part in which the balls are located between the sleeve and the tap enclosed thereby, and one return part in which the balls are entirely enclosed in the sleeve.
  • FIG. 1 only the return parts of the ball races are shown whereas FIG. 2 shows in section how the various ball race parts are located in relation to each other.
  • the slide 40 is provided with recesses limited by envelope surfaces 46, 48 which closely contact and seal against the periphery of the rotors 24 and 26, respectively.
  • the slide 40 is directly connected by means of a rod 50 with a supporting ring 52 movably arranged in a cylinder 54 which is closed at one end and at its other end is open to the inlet chamber 16.
  • the supporting ring 52 is not arranged to seal against the cylinder 54 but instead thesame pressure is prevailing on both sides of the supporting ring.
  • One end of each of the two springs 56, 58 is contacting the closed end of the cylinder 54.
  • the other end of one 56 of the springs is always contacting the supporting ring 52 whereas the other spring 58 is so short that its other end will contact the supporting ring 52 only when this has been displaced from its position correspond ing to the largest inlet opening 18 in direction to decreasing inlet opening. 'In the position shown in FIG. 1, however, both springs are cont-acting the supporting ring 52.
  • the slide will be actuated by one spring only during the first part of its movement and during the latter part of its movement by both springs simultaneously.
  • one or more springs may possibly be arranged to be connected gradually during the movement.
  • the expansion ratio of the motor is greater due to a greater change in volume of the expansion chamber as it moves between the inlet 18 and the outlet 14. Because of this increased expansion ratio and the reduced area of the inlet 18, the volume of gas fluid moving through the motor will be reduced. Conversely, as the pressure in chamber 16 is reduced, the piston will move to the left causing the slide to move to the left, which in turn reduces the expansion ratio, increases the area of inlet 18 and allows a greater volume of gas to be carried through the motor.
  • Chamber 16 is connected by a conduit to a compressor operated by the airplane power unit. At low altitudes the pressure differential between the chamber 16 and the outside atmosphere is greater than at higher altitudes. Therefore, on the ground the piston 16 and the slide 40 will be forced to the right until balanced by the springs 56 and 58. Hence, as-
  • the expansion ratio of the motor will be greater and the volume of gas delivered through the motor will be less.
  • the pressure differential between chamber 16 and the atmosphere is reduced so that the piston 60 moves to the left, moving the slide 40 to the left so that the expansion ratio of the motor is less, the inlet opening 18 is greater and a larger volume or gas is delivered through the motor.
  • the rod is further provided with an extension formed as a piston and pasing through a hole 64 which is provided with seals 62 in the closed end of the cylinder 54.
  • the free end of the extension 60 is influenced by the reference medium pressure prevailing outside the cylinder 54.
  • the extension 60 is designed to a larger diameter than the rod 50 so that due to the diiferent areas the supporting ring 52 is moved in relation to the pressure difierence between the pressure in the inlet chamber 16 and the reference medium pressure.
  • cylinder 54 and the extension 60 of rod 50 are sewing as guides for the springs 56 and 58, respectively.
  • FIG. 3 shows in a pv-diagram in what manner the difference between the built-in pressure ratio and the actual pressure ratio injuriously will influence the mode of the expansion.
  • the operating medium is expanded from the theoretically appropriate inlet pressure 1 along the continuous line.
  • the operating medium would expand along the lower dash line.
  • an expansion is obtained along the ideally continuous line, giving a higher efliciency and in addition causing a greater gas quantity to pass through the device.
  • the power which has to be consumed by means of the fan will thus increase, which in turn involves a higher engine speed and an additionally increased gas flow.
  • the operating medium would expand along the upper dash line.
  • the expansion instead to commence at an inlet volume corresponding to a built-in pressure ratio 11 an expansion is obtained along the ideally continuous line involving a higher efficiency and in addition causing a smaller gas quantity to pass through the machine, i.e. that less work need be sacrificed in order to obtain the cooling effect desired.
  • FIG. 4 shows in a diagram by means of the continuous curve in what manner the built-in pressure ratio will vary with the size of the inlet opening.
  • the broken curve shows how the position of the slide actually varies with a control device provided with three springs.
  • a pressure difference m-p... between the inlet pressure p; and the reference medium pressure pm the slide is moved to a position corresponding to a built-in pressure ratio 1r Since the counter pressure 12 and the reference medium pressure is will never substantially exceed 1, corresponding to the pressure at the ground level, the number value of p /p must always be greater than the number value of pi--p
  • the number value of the built-in pressure ratio 1r can never exceed the number value of J -pm, when the control device has been designed in accordance with the diagram in FIG. 4. Therefore the actual pressure ratio p /p can never be less than the built-in pressure ratio in with such a control device.
  • FIG. 5 shows two efliciency curves dependent of the actual pressure ratio for expansion devices of prwent type with different built-in pressure ratios. It is evident from these curves that the efiiciency subsides considerably quicker at a too low actual pressure ratio than at a too high actualpressure ratio, for which reason it is desirable to have a somewhat too high actual pressure ratio rather than a too low ratio in devices of the present type,
  • FIG. 5 shows that in case the number value of p /p considerably exceeds the number value of l -pm which occurs at high altitudes, then the efiiciency in spite of this is still acceptable.
  • a rotary screw type pump having a casing structure providing intersecting cylindrical bores having parallel axes and high pressure and low pressure openings communicating with said bores and having a pair of helically ribbed rotors disposed in said bores to rotate in intermeshed relation in said bores and to co-operate With each other and with the Walls of said bores in a manner to sealingly separate the high pressure and low pressure openings to form variable volume chambers defined by the walls of said bores and the surfaces of said rotors, said chambers being in communication alternately with the high pressure opening and with the low pressure opening as the rotors rotate, the improvement comprising a sliding member disposed in said casing, said sliding member forming a portion of the inner walls of said bores adjacent one of said openings and defining in part the size of said opening, means for adjusting said member in one direction to reduce the area of the bore walls in contact with the rotors to increase the size of said opening adjacent said member and for adjusting said member in the opposite direction to increase the
  • a rotary screw type pump having a casing structure providing intersecting cylindrical bores having parallel axes and high pressure and low pressure openings communicating with said bores and having a pair of helically ribbed rotors disposed in said bores to rotate in intermeshed relation in said bores and to co-operate with each other and with the walls of said bores in a manner to sealingly separate the high pressure and low pressure openings to form variable volume chambers defined by the walls of said bores and the surfaces of said rotors, said chambers being in communication alternately with the high pressure opening and with the low pressure opening as the rotors rotate, the improvement comprising a sliding member disposed in said casing, said sliding member forming a portion of the inner Walls of said bores adjacent one of said openings and defining in part the size of said opening, means for adjusting said member in one direction to reduce the area of the bore walls in contact with the rotors to increase the size of said opening adjacent said member and for adjusting said member in the opposite direction to increase the
  • said pressure responsive means for adjusting the sliding member comprises a sliding piston which reciprocates responsive to changes in the pressure differential between the inside of the casing at the opening adjacent the slide and the reference pressure outside the casing, and means for operating the sliding member in response to reciprocal motion of the piston.
  • said pressure responsive means for adjusting the sliding member includes means responsive to the atmospheric pressure.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Discharge By Other Means (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
  • Preliminary Treatment Of Fibers (AREA)
US795530A 1958-02-27 1959-02-25 Rotary device, such as refrigerating machine or similar device Expired - Lifetime US3045447A (en)

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SE194058 1958-02-27

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US (1) US3045447A (fr)
BE (1) BE576047A (fr)
CH (1) CH378909A (fr)
DE (1) DE1102762B (fr)
FR (1) FR1224331A (fr)
GB (1) GB860668A (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3151806A (en) * 1962-09-24 1964-10-06 Joseph E Whitfield Screw type compressor having variable volume and adjustable compression
US3314597A (en) * 1964-03-20 1967-04-18 Svenska Rotor Maskiner Ab Screw compressor
US3432089A (en) * 1965-10-12 1969-03-11 Svenska Rotor Maskiner Ab Screw rotor machine for an elastic working medium
US3473322A (en) * 1966-09-09 1969-10-21 Sulzer Ag Supercharged internal combustion piston engine
US3549280A (en) * 1968-01-03 1970-12-22 Gutehoffnungshuette Sterkrade Screw machine
DE2331830A1 (de) * 1972-06-30 1974-01-17 Stal Refrigeration Ab Schraubenkompressor
US4498849A (en) * 1980-06-02 1985-02-12 Sullair Technology Ab Valve arrangement for capacity control of screw compressors
US4802457A (en) * 1985-10-14 1989-02-07 Svenska Rotor Maskiner Ab Internal combustion engine provided with a supercharger
WO1996016302A1 (fr) * 1994-11-17 1996-05-30 Svenska Rotor Maskiner Ab Systeme et procede de refrigeration
WO1996026398A1 (fr) * 1995-02-20 1996-08-29 Svenska Rotor Maskiner Ab Systeme a cycle d'air refroidi et procede d'exploitation d'un tel systeme
US6176695B1 (en) * 1997-02-05 2001-01-23 Rotary Power Couple Engines Limited Control of a lobed rotor machine
US20050126204A1 (en) * 2003-12-12 2005-06-16 Visteon Global Technologies, Inc. Air-cycle air conditioning system for commercial refrigeration
EP1934472A1 (fr) * 2005-09-07 2008-06-25 Carrier Corporation Distributeur à tiroir

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106801619A (zh) * 2017-03-03 2017-06-06 上海维尔泰克螺杆机械有限公司 容积比可调的螺杆膨胀机

Citations (8)

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Publication number Priority date Publication date Assignee Title
US678570A (en) * 1900-10-22 1901-07-16 William Anthony Jones Motor.
US996169A (en) * 1911-06-27 Herbert Van Deventer John Rotary engine.
US2425000A (en) * 1943-03-27 1947-08-05 Joy Mfg Co Apparatus for automatically controlling pressure and temperature within aircraft cabins
US2477004A (en) * 1945-10-20 1949-07-26 Joy Mfg Co Screw type air pump
US2585570A (en) * 1946-07-29 1952-02-12 Lockheed Aircraft Corp Aircraft pressurizing and cooling system
US2656972A (en) * 1949-01-31 1953-10-27 Dresser Ind Adjustable port arrangement for the high-pressure ends of fluid pumps and motors of the rotary screw type
US2808813A (en) * 1952-05-21 1957-10-08 Svenska Rotor Maskiner Ab Rotary positive displacement engine with helically grooved cooled rotors
US2896903A (en) * 1957-03-05 1959-07-28 Otis Eng Co Cut-off device

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE188320C (fr) *
DE125021C (fr) *
DE406869C (de) * 1923-11-30 1924-12-06 Felix Langen Steuerung fuer Drehkolbenmaschinen
US1583232A (en) * 1924-02-15 1926-05-04 Sullivan Machinery Co Compressor
DE733265C (de) * 1941-04-30 1943-03-23 Wilhelm Knapp G M B H Maschf Umsteuerbarer Druckluftmotor mit drei gemeinsam umlaufenden Zahnradlaeuferpaaren

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US996169A (en) * 1911-06-27 Herbert Van Deventer John Rotary engine.
US678570A (en) * 1900-10-22 1901-07-16 William Anthony Jones Motor.
US2425000A (en) * 1943-03-27 1947-08-05 Joy Mfg Co Apparatus for automatically controlling pressure and temperature within aircraft cabins
US2477004A (en) * 1945-10-20 1949-07-26 Joy Mfg Co Screw type air pump
US2585570A (en) * 1946-07-29 1952-02-12 Lockheed Aircraft Corp Aircraft pressurizing and cooling system
US2656972A (en) * 1949-01-31 1953-10-27 Dresser Ind Adjustable port arrangement for the high-pressure ends of fluid pumps and motors of the rotary screw type
US2808813A (en) * 1952-05-21 1957-10-08 Svenska Rotor Maskiner Ab Rotary positive displacement engine with helically grooved cooled rotors
US2896903A (en) * 1957-03-05 1959-07-28 Otis Eng Co Cut-off device

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3151806A (en) * 1962-09-24 1964-10-06 Joseph E Whitfield Screw type compressor having variable volume and adjustable compression
US3314597A (en) * 1964-03-20 1967-04-18 Svenska Rotor Maskiner Ab Screw compressor
US3432089A (en) * 1965-10-12 1969-03-11 Svenska Rotor Maskiner Ab Screw rotor machine for an elastic working medium
US3473322A (en) * 1966-09-09 1969-10-21 Sulzer Ag Supercharged internal combustion piston engine
US3549280A (en) * 1968-01-03 1970-12-22 Gutehoffnungshuette Sterkrade Screw machine
DE2331830A1 (de) * 1972-06-30 1974-01-17 Stal Refrigeration Ab Schraubenkompressor
US4498849A (en) * 1980-06-02 1985-02-12 Sullair Technology Ab Valve arrangement for capacity control of screw compressors
US4802457A (en) * 1985-10-14 1989-02-07 Svenska Rotor Maskiner Ab Internal combustion engine provided with a supercharger
WO1996016302A1 (fr) * 1994-11-17 1996-05-30 Svenska Rotor Maskiner Ab Systeme et procede de refrigeration
US5732560A (en) * 1994-11-17 1998-03-31 Svenska Rotor Maskiner Ab System and method for performing cooling
WO1996026398A1 (fr) * 1995-02-20 1996-08-29 Svenska Rotor Maskiner Ab Systeme a cycle d'air refroidi et procede d'exploitation d'un tel systeme
US5642629A (en) * 1995-02-20 1997-07-01 Svenska Rotor Maskiner Ab Cooled air cycle system and method for operating such a system
US6176695B1 (en) * 1997-02-05 2001-01-23 Rotary Power Couple Engines Limited Control of a lobed rotor machine
US20050126204A1 (en) * 2003-12-12 2005-06-16 Visteon Global Technologies, Inc. Air-cycle air conditioning system for commercial refrigeration
US6966198B2 (en) 2003-12-12 2005-11-22 Visteon Global Technologies, Inc. Air-cycle air conditioning system for commercial refrigeration
EP1934472A1 (fr) * 2005-09-07 2008-06-25 Carrier Corporation Distributeur à tiroir
EP1934472A4 (fr) * 2005-09-07 2012-04-11 Carrier Corp Distributeur à tiroir

Also Published As

Publication number Publication date
BE576047A (fr) 1959-08-24
FR1224331A (fr) 1960-06-23
GB860668A (en) 1961-02-08
CH378909A (de) 1964-06-30
DE1102762B (de) 1961-03-23

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